Retention of Ball Bearing Cartridge for Turbomachinery

ABSTRACT

An exemplary method for limiting movement of an outer race of a bearing cartridge includes positioning the bearing cartridge in a substantially cylindrical bore having a longitudinal axis, an inner diameter exceeding an outer diameter of the outer race, a proximate end and a distal end; limiting axial movement of the outer race at the distal end of the cylindrical bore with a counterbore substantially coaxial to the cylindrical bore and having an inner diameter less than the outer diameter of the outer race; limiting axial movement of the outer race at the proximate end of the cylindrical bore with a plate positioned substantially orthogonal to the longitudinal axis; and limiting rotation of the outer race with a pin positioned in a pin opening accessible via a lubricant drain. Various exemplary bearing cartridges, housings, assemblies, etc., are also disclosed.

RELATED APPLICATION

This application is a divisional application of, and claims the benefit of, co-pending U.S. patent application Ser. No. 11/683,615, filed Mar. 8, 2007, which is incorporated herein by reference, which is a divisional application of, and claims the benefit of, U.S. patent application Ser. No. 10/879,253, filed Jun. 28, 2004 (now U.S. Pat. No. 7,214,037, issued May 8, 2007), which is incorporated herein by reference.

TECHNICAL FIELD

Subject matter disclosed herein relates generally to turbomachinery for internal combustion engines and, in particular, rolling element bearing cartridges and bearing housings for such bearing cartridges.

BACKGROUND

The advantages associated with low friction bearings are well known to a multitude of varied industries. High-speed applications with DN (dynamic number) values over 1,000,000 are common place for turbomachinery. These high-speed applications, owing to the fact that rotor imbalance force increases as a square function of rotor speed, require damping. Without damping, transmitted forces through the system would cause many well-known problems such as noise, fretting, loosening of joints, and overall reduced service life. Further, the bearings themselves would have unacceptable life. For these reasons, turbomachinery bearings are not hard mounted within their housings. The skilled rotordynamics design engineer spends the majority of his/her life managing these forces, especially those forces encountered as the rotor goes through its natural frequencies, commonly referred to as “critical speeds”.

Most turbochargers that employ a low friction rolling element bearing use two angular contact ball bearings, with each accepting the thrust load in a given axial direction, that are joined together in what is commonly referred to as a “cartridge”. In a cylindrical coordinate system a bearing may be defined with respect to axial, radial and azimuthal dimensions. Within a bearing housing, referred to as housing in subsequent text, a cartridge is located axially and azimuthally via one or more mechanisms. For proper functioning, some movement can occur in a radial direction along a radial line typically defined by an azimuthal locating mechanism.

Conventional bearing cartridge and housing assemblies typically rely on an axial thrust load pin to locate the cartridge axially and azimuthally within a housing. Such pins have a limited ability to align the cartridge in a housing and receive most of the thrust load. Consequently, axial thrust load pins can raise serious wear and misalignment issues.

Overall, an industry need exists for rolling element bearings and/or housings that allow for better alignment and/or reduced wear. Various exemplary bearing cartridges and housings presented herein address such issues and optionally other issues.

BRIEF DESCRIPTION OF THE DRAWINGS

A more complete understanding of the various methods, devices, systems, arrangements, etc., described herein, and equivalents thereof, may be had by reference to the following detailed description when taken in conjunction with the accompanying drawings wherein:

FIG. 1A is a perspective view diagram of a prior art bearing cartridge for a turbocharger.

FIG. 1B is a diagram of a prior art bearing cartridge in a prior art housing.

FIG. 2 is a perspective view diagram of an exemplary bearing cartridge that does not include an aperture to receive an axial thrust load pin.

FIG. 3 is a side view of an exemplary bearing cartridge that does not include an aperture to receive an axial thrust load pin.

FIG. 4 is a cross-sectional view of an exemplary assembly that includes an exemplary housing and an exemplary bearing cartridge.

FIG. 5 is a cross-sectional view of an exemplary housing that includes features for axially locating a bearing cartridge.

FIG. 6 is front view of an exemplary housing assembly that includes a retaining mechanism that acts to axially locate a bearing cartridge in the housing assembly.

FIG. 7 is a cross-sectional side view of an exemplary retaining mechanism that acts to axially locate a bearing cartridge in a housing.

FIG. 8 is a cross-sectional side view of an exemplary bearing cartridge that includes various outer surface regions.

FIG. 9A is a cross-sectional side view of an exemplary housing that includes two regions with different inner diameters to thereby allow for formation of, for example, two film regions in conjunction with a bearing cartridge.

FIG. 9B is a cross-sectional top view of an exemplary housing that includes two regions with different inner diameters to thereby allow for formation of, for example, two film regions in conjunction with a bearing cartridge.

DETAILED DESCRIPTION

Various exemplary methods, devices, systems, arrangements, etc., disclosed herein address issues related to technology associated with turbochargers and are optionally suitable for use with electrically assisted turbochargers.

FIG. 1A shows a perspective view of prior art bearing cartridge 100. A cylindrical coordinate system is shown for reference that includes radial (r), axial (x) and azimuthal (Θ) dimensions. The cartridge 100 includes two annular wells 104, 104′ positioned on an outer race 105 intermediate a center section 106 and respective ends of the cartridge 100. The center section 106 of the cartridge 100 includes an opening 108 that cooperates with a pin to position the cartridge 100 axially and azimuthally in a housing or journal. For example, conventional bearing cartridges for turbomachinery often rely on an axial thrust load pin that is received by such an opening to axially locate the bearing cartridge in a conventional housing.

The wells 104, 104′ are positioned adjacent to outer sections 110, 110′ of the outer race 105, respectively. The outer sections 110, 110′ have equal outer diameters that define a clearance with a housing and thereby allow for formation of lubricant films f, f′.

FIG. 1B shows a cross-sectional view of the prior art cartridge 100 in a prior art housing 160. A pin 162 acts to locate the cartridge 100 axially and azimuthally while allowing freedom in the radial direction. In particular, the pin 162 cooperates with the outer race 105. Axial thrust load along the x-axis causes force to be transmitted from the outer race 105 of the bearing cartridge 100 to the housing 160 via the pin 162. As the pin allows for radial movement, some small amount of clearance exists between the outer diameter of the pin 162 and the inner diameter of the opening 108. Consequently, during operation thrust may cause axial movement of the cartridge with respect to the housing. Such movement can contribute to wear and misalignment.

The pin 162 also allows for lubricant to flow via a conduit in the pin 162 to a lubricant entrance well 164 adjacent the center section 106 of the cartridge 100. A lubricant exit well 168 exists nearly opposite the entrance well 164 that allows for drainage of lubricant in and about the cartridge 100.

As shown in FIG. 1B, a clearance exists between an outer diameter of the outer sections 110, 110′ and an inner diameter of the housing 160. In this prior art assembly, the clearance defines a single film thickness f. An enlargement of the cross-section shows the single film thickness f as it exists on either side of the well 104. The selection of this clearance (squeeze film thickness) acts to determine the operational characteristics such as rotor radial freedom and damping of rotor imbalance forces.

FIG. 2 shows a perspective view on an exemplary bearing cartridge 200 that does not include an opening for receiving an axial thrust load pin. The cartridge 200 includes two annular wells 204, 204′ positioned on an outer race 205 intermediate a center section 206 and respective ends of the cartridge 200. In this example, the cartridge 200 includes openings 207 and 207′ that allow jet lubrication to enter and be directed at the balls of the cartridge 200. Additional openings are optionally included for lubricant flow.

The wells 204, 204′ are positioned adjacent to end sections 210, 210′, respectively. The end sections 210, 210′ of the outer race 205 have outer diameters that can define clearances with a housing and thereby allow for formation of lubricant films f1, f1′, which may be substantially equal.

FIG. 3 shows a side view of an exemplary cartridge 300 such as the cartridge 200 of FIG. 2. The cartridge 300 includes an outer race 305 having an approximate length L, an approximate axial midpoint Lm and including end sections 310, 310′ having outer diameters D_(O) 1, D_(O) 1′. In this example, a drain or lubricant opening 309 is positioned at an axial position at or proximate to the midpoint Lm. The cartridge 300 may include openings such as 207, 207′ of the cartridge 200 of FIG. 2. The lubricant opening 309 optionally receives a pin or other device to limit rotation of the outer race 305. The lubricant opening 309 may receive such a rotation limiting device while still being capable of some radial movement.

The cartridge 300 includes wells of axial width Δ_(w) 1, Δ_(w) 1′ exist between a center section 306 and end sections 310, 310′ with outer diameters D_(O) 1 and D_(O) 1′. The well widths Δ_(w) 1, Δ_(w) 1′ may be substantially equal. The outer sections 310, 310′ may differ in axial width. For example, the cartridge 300 may include an outer section 310 with outer diameter D_(O) 1 that has an axial width less than the outer section 310′ with outer diameter D_(O) 1′.

The exemplary cartridge 300 includes various parameters that may be used to achieve desired performance characteristics. For example, the axial width and outer diameters of the various sections may be used to define radial clearances/film thicknesses and axial film length(s). In general, judicious selection of thickness, length and number of squeeze films can act to achieve suitable reduction in radial freedom and optimized damping of rotor imbalance forces. Various examples capable of multiple squeeze film thicknesses are described further below with respect to FIG. 8 and FIGS. 9A-B.

FIG. 4 shows a cross-sectional diagram of an exemplary assembly 400 of a turbomachinery device. The assembly 400 includes a bearing cartridge 300 positioned in a housing 440 and located axially with aid of a plate 450. In this example, the plate 450 abuts a surface 446 of the housing 440. A pin 460 received by an opening 444 of the housing 440 optionally aids in locating the cartridge 300 azimuthally with respect to the housing 440. The opening 444 optionally comprises a pin opening having an axis that intersects the central axis (e.g., x-axis) at an angle φ, which is optionally non-orthogonal.

In this example, the cartridge 300 is located axially with aid of a counterbore 442 of the housing 440 and the plate 450. In general, the plate 450 and the counterbore 442 define an axial distance that is greater than the axial length of the outer race of the bearing cartridge 300. Proper operation of the assembly 400 requires some amount of radial movement; consequently, the axially locating mechanism allows the bearing cartridge to move radially. Further, a clearance may be defined by the difference between the axial distance between a surface of the plate 450 and a surface of the counterbore 442 and the axial length of the outer race of the bearing cartridge 300. Adjustment to such a clearance may be possible via a fixation mechanism of the plate 450 (see, e.g., bolt 452) and/or other features (e.g., gaskets, spacers, etc.).

Various features of the exemplary assembly 400 also act to directly distribute axial thrust loads to more than one component. For example, the plate 450 can receive thrust loads and the counterbore 442 of the housing 440 can receive axial thrust loads from the bearing cartridge 300. In comparison, the conventional assembly of FIG. 1B transmits axial thrust loads directly and solely to the pin 162. In addition, the exemplary assembly 400 can distribute axial thrust loads over greater surface area when compared to the pin 162 of the conventional assembly of FIG. 1B.

As already mentioned, the housing 440 includes an opening 444 that can receive the pin 460 to aid in azimuthal location of the outer race of the bearing cartridge 300. Such a pin may be referred to as an anti-rotation pin or an azimuthal locating pin because it acts to locate azimuthally and limit rotation of an outer race of a bearing cartridge with respect to a housing. In this example, a lubricant drain opening 448 of the housing 440 allows for insertion of the pin 460 in the opening 444. In this manner, the lubricant drain opening 448 allows drainage of lubricant and insertion and/or adjustment of an anti-rotation pin. While a straight line shows access to the opening 444, access is optionally indirect (e.g., not along a straight line).

FIG. 5 shows a cross-sectional top view of an exemplary housing 440 and a plate 450. The exemplary housing 440 includes a proximate recessed surface 446 and a distal counterbore 442. The proximate recessed surface 446 is optionally associated with a compressor side of a turbomachinery device and the distal counterbore 442 is optionally associated with a turbine side of a turbomachinery device. Of course, other arrangements are possible.

The exemplary housing 440 includes an opening 444 set an angle to a central longitudinal housing axis (e.g., x-axis) that allows for insertion of a pin. Such a pin may act to azimuthally locate an outer race of a bearing cartridge in the exemplary housing 440.

The exemplary housing 440 includes an attachment mechanism for the plate 450. In this example, threaded holes 445, 445′ are providing that open along the surface 446. The holes 445, 445′ receive bolts 452, 452′, respectively. Washers 453, 453′ are also shown in this example. Other attachment mechanisms may be used for attaching a plate or limiting mechanism to a housing. Further, while a substantially circular shaped plate is shown, other shapes or limiting mechanisms are possible and may include one or more surfaces and/or one or more components that act to limit movement of an outer race of a bearing cartridge in the cylindrical bore of a housing in conjunction with a counterbore. An exemplary housing optionally includes an attachment mechanism or mechanisms for one or more limiting components that extend radially inward to a minimum radius less than the inner radius of a cylindrical bore wherein at least some of the components can act to limit axial movement of a bearing cartridge in the cylindrical bore.

FIG. 6 shows a front view of an exemplary assembly 600 that includes an exemplary housing 440 and an exemplary plate 450. In this example, the plate 450 fits in a recess of the housing 440. The plate 450 acts to define an axial distance along with a counterbore of the housing (not shown in FIG. 6, see, e.g., FIG. 5). In conjunction with an axial length of an outer race of a bearing cartridge, the axial distance acts to define a clearance or clearances between the outer race and the plate 450 and/or the counterbore of the housing 440. The exemplary plate 450 includes four openings 454, 454′, 454″, 454′″ for use in securing the plate 450 to the housing 440. A bolt 452 or other device passes through the opening 454′″ to secure the plate 450 to the housing 440. In this example, a washer 453 cooperates with the bolt 452 to secure the plate 450.

The plate 450 includes an opening 456 that has an inner diameter less than the inner diameter of a substantially cylindrical bore of the housing 440. In this example, the opening 456 is substantially coaxial with the cylindrical bore of the housing 440. A counterbore 442 of the housing 440 has an inner diameter less than the inner diameter of the cylindrical bore of the housing 440. In this example, the counterbore 442 has an arc length less than 360 degrees. Exemplary counterbores may include one or more arc segments, protrusions, etc., that extend inwardly toward a longitudinal or center axis of the cylindrical bore to thereby limit movement of an outer race of a bearing cartridge in the cylindrical bore.

FIG. 7 shows an exemplary assembly 700 that includes an exemplary plate 750. In this example, the plate 750 is a compressor backplate that fits into the recessed region of a housing 440, for example, at a surface 446. In this example, an attachment mechanism includes use of blots 752, 752′ to secure the plate 750 to the housing 440. The plate 750 extends radially inward past the surface 446 where it further extends past at least a portion of an outer race 305 of a bearing cartridge. The plate 750 includes an opening that has an inner dimension (e.g., a diameter, etc.) that is less than the outer diameter of the outer race 305. While an exemplary plate may include a substantially circular opening with a diameter less than that of an outer race of a bearing cartridge, various exemplary plates may include other shapes, protrusions, etc., that extend inwardly past an inner diameter of a substantially cylindrical bore of a housing to thereby limit axial movement of an outer race of a bearing cartridge. For example, an exemplary plate optionally includes one or more protrusions that extend radially inward toward a central axis to limit movement of an outer race of a bearing cartridge. While not shown in FIG. 7, the housing 440 optionally includes a counterbore to limit movement of the outer race 305, for example, where the plate 750 is positioned at a proximate end of a substantially cylindrical bore of a housing and the counterbore is positioned at distal end of the substantially cylindrical bore of the housing (see, e.g., the counterbore 442 of FIG. 5). Further, the housing 440 of FIG. 7 optionally includes an opening such as the opening 444 of FIG. 5 (e.g., a pin opening, etc.). While such an opening is sometimes referred to herein as a “pin” opening, the term pin may optionally refer to various mechanisms such as screws, bolts, etc., that act to limit rotation of an outer race of a bearing cartridge.

FIG. 8 shows a cross-sectional diagram of an exemplary bearing cartridge 800 that allows for multiple films of optionally different thicknesses. The cartridge 800 includes a center section 806, intermediate sections 810, 810′ and outer sections 812, 812′. The bearing also includes lubricant passages 807, 807′ and 809.

An enlargement shows various wells (e.g., wells, grind reliefs, etc.) and/or transitions from a first outer diameter to a second outer diameter. A wall 866 of a housing or journal having an inner diameter acts to define clearances and film thicknesses f1, f2. In a first scenario 801, wells have curvilinear cross-section; in a second scenario 802, wells have substantially polygonal cross-section; and in a third scenario 803, a step in outer diameter exists between a thick film region f1 and a thinner film region f2. The scenarios 801, 802, 803 are exemplary as others may be used to create clearances that form multiple film thicknesses.

A housing or journal may act to define clearances that form multiple film thicknesses between the housing and one or more outer diameters of a bearing cartridge. For example, an exemplary housing may include two or more inner diameters that act to define more than one annular clearance with a bearing cartridge and a counterbore to help axially locate the bearing cartridge and/or an opening for receiving a pin to help azimuthally locate an outer race of the bearing cartridge.

FIG. 9A shows a cross-sectional, side view of an exemplary housing 940 and FIG. 9B shows a cross-sectional top view of the exemplary bearing housing 940. The exemplary housing 940 can house a bearing cartridge and act to define clearances between an outer surface of the bearing cartridge and an inner wall of the housing 940 wherein the clearances act to form various films that can be aimed at reduction of unwanted excessive radial clearance and/or optimized damping of rotor imbalance forces.

The exemplary housing 940 includes a counterbore 942, an opening 944 and a surface 946 substantially perpendicular to a central axis (e.g., x-axis). The opening 944 optionally comprises a pin opening having an axis that intersects the central axis at an angle φ, which is optionally non-orthogonal. The surface 946 and the counterbore 942 may define a distance that in combination with a bearing cartridge acts to define an axial clearance. A plate (see, e.g., the plate 450 of FIG. 6) or other component optionally cooperates with the surface 946 to define a proximate end of a bearing cartridge chamber while the counterbore 942 defines a distal end of the bearing cartridge chamber.

The bearing cartridge chamber includes an inner surface 966 that has a first inner diameter and an inner surface 967 that has a second inner diameter wherein the first inner diameter exceeds the second inner diameter. A bearing cartridge that includes an outer surface having an outer diameter may act to define annular clearances with the first and second inner surfaces 966, 967 when positioned in the housing to form an assembly.

Various exemplary devices, methods, systems, arrangements, etc., described herein pertain to formation and use of multiple film thicknesses. In various examples, one film has damping characteristics and another film has characteristics that minimize excessive radial freedom and play.

An exemplary bearing cartridge includes an inner film to outer film ratio of approximately 1:2, i.e., the inner film being approximately twice the thickness of the outer film. For example, an inner film of approximately 0.0030 inch (approx. 0.076 mm) and an outer film of approximately 0.0015 inch (approx. 0.0038 mm) wherein the inner film acts to dampen vibrations and the outer film acts to limit rotor radial play. Such an exemplary bearing cartridge may be suitable for use in a commercially available GARRETT® GTA47-55R turbomachinery device (Torrance, Calif.).

In general, a sufficiently thick film can act to reduce noise and vibration and loading through the system; whereas a thinner film can reduce slop or play in the system (e.g., rotor play, etc.). A thinner film may also allow for reduction in wheel to housing clearances in a turbocharger system, which can act to reduce undesirable secondary aerodynamic flows that would cause reduced compressor and turbine stage thermodynamic efficiencies.

Various examples include one or more thinner clearance regions proximate to an outer end(s) of a bearing cartridge. A pair of thinner clearance regions proximate to outer ends of a bearing cartridge may limit pivot when compared to a thinner clearance region(s) positioned proximate to or at a center section.

Although some exemplary methods, devices, systems arrangements, etc., have been illustrated in the accompanying Drawings and described in the foregoing Detailed Description, it will be understood that the exemplary embodiments disclosed are not limiting, but are capable of numerous rearrangements, modifications and substitutions without departing from the spirit set forth and defined by the following claims. 

1. A method of limiting movement of an outer race of a bearing cartridge comprising: positioning the bearing cartridge in a substantially cylindrical bore having a longitudinal axis, an inner diameter exceeding an outer diameter of the outer race, a proximate end and a distal end; limiting axial movement of the outer race at the distal end of the cylindrical bore with a counterbore substantially coaxial to the cylindrical bore and having an inner diameter less than the outer diameter of the outer race; limiting axial movement of the outer race at the proximate end of the cylindrical bore with a plate positioned substantially orthogonal to the longitudinal axis; and limiting rotation of the outer race with a pin positioned in a pin opening accessible via a lubricant drain.
 2. The method of claim 1 wherein the pin axis substantially intersects the longitudinal axis of the cylindrical bore at a non-orthogonal angle.
 3. The method of claim 1 wherein the outer race comprises an opening to receive the pin.
 4. The method of claim 1 further comprising providing lubricant and forming lubricant films between the outer race and the bore.
 5. The method of claim 4 wherein the forming forms lubricant films that comprise different film thicknesses.
 6. The method of claim 1 further comprising: providing lubricant; forming a first lubricant film between the outer race and the bore and limiting radial freedom of the bearing using the first lubricant film; and forming a second lubricant film between the outer race and the bore and damping bearing vibrations using the second lubricant film.
 7. The method of claim 6 comprising providing a first annular clearance between the outer race and the bore to determine thickness of the first lubricant film and providing a second annular clearance between the outer race and the bore to determine thickness of the second lubricant film.
 8. The method of claim 1 further comprising: providing lubricant; forming a first lubricant film in an annular clearance between the outer race; and forming a second lubricant film in an annular clearance between the outer race, wherein thickness of the first lubricant film differs from thickness of the second lubricant film.
 9. The method of claim 8 further comprising reducing noise, vibration and loading by a thicker of the lubricant films.
 10. The method of claim 8 further comprising limiting radial freedom of the bearing in the bore by a thinner of the lubricant films.
 11. The method of claim 8 wherein the thickness of the second lubricant film is thicker than the thickness of the first lubricant film by a factor of approximately
 2. 12. The method of claim 8 wherein the first lubricant film is thicker than the thickness of the second lubricant film and wherein the second lubricant film forms adjacent to the distal end of the bore or adjacent to the proximate end of the bore.
 13. The method of claim 8 further comprising forming a pair of lubricant films having approximately the same thickness and limiting radial freedom of the bearing in the bore using the pair of lubricant films wherein the pair comprises the first lubricant film and damping bearing vibration using the second lubricant film.
 14. A method comprising: positioning a bearing cartridge in a substantially cylindrical bore having a longitudinal axis, an inner diameter exceeding an outer diameter of the outer race, a proximate end and a distal end; limiting axial movement of the outer race at the distal end of the cylindrical bore with a counterbore substantially coaxial to the cylindrical bore and having an inner diameter less than the outer diameter of the outer race; limiting axial movement of the outer race at the proximate end of the cylindrical bore with a plate positioned substantially orthogonal to the longitudinal axis; limiting rotation of the outer race with a pin positioned in a pin opening accessible via a lubricant drain; and providing annular clearances between the outer race and the bore configured to form a pair of lubricant films to limit radial freedom of the bearing cartridge in the bore and to form at least one lubricant film to damp vibrations of the bearing cartridge in the bore.
 15. The method of claim 14 further comprising providing the annular clearances to position at least one of the at least one lubricant film to damp vibrations between the pair of lubricant films to limit radial freedom.
 16. The method of claim 14 further comprising providing lubricant and rotating a turbocharger shaft seated in the bearing cartridge.
 17. The method of claim 16 further comprising limiting radial freedom and damping vibrations while rotating the turbocharger shaft.
 18. The method of claim 14 wherein the annular clearances configured to form the pair of lubricant films have a radial dimension of approximately one half the annular clearance configured to form one of the at least one lubricant films to damp vibrations. 